EP2021744A2 - Appareil de mesure d'écoulement - Google Patents

Appareil de mesure d'écoulement

Info

Publication number
EP2021744A2
EP2021744A2 EP07761599A EP07761599A EP2021744A2 EP 2021744 A2 EP2021744 A2 EP 2021744A2 EP 07761599 A EP07761599 A EP 07761599A EP 07761599 A EP07761599 A EP 07761599A EP 2021744 A2 EP2021744 A2 EP 2021744A2
Authority
EP
European Patent Office
Prior art keywords
fluid
piston
flow
valve
measuring apparatus
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP07761599A
Other languages
German (de)
English (en)
Other versions
EP2021744A4 (fr
Inventor
Mark W. Kirchner
John D. Tomlinson
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sko Flo Industries Inc
SKO FLO Ind Inc
Original Assignee
Sko Flo Industries Inc
SKO FLO Ind Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sko Flo Industries Inc, SKO FLO Ind Inc filed Critical Sko Flo Industries Inc
Publication of EP2021744A2 publication Critical patent/EP2021744A2/fr
Publication of EP2021744A4 publication Critical patent/EP2021744A4/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F15/00—Details of, or accessories for, apparatus of groups G01F1/00 - G01F13/00 insofar as such details or appliances are not adapted to particular types of such apparatus
    • G01F15/005—Valves
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F25/00—Testing or calibration of apparatus for measuring volume, volume flow or liquid level or for metering by volume
    • G01F25/10—Testing or calibration of apparatus for measuring volume, volume flow or liquid level or for metering by volume of flowmeters
    • G01F25/11—Testing or calibration of apparatus for measuring volume, volume flow or liquid level or for metering by volume of flowmeters using a seal ball or piston in a test loop
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01F—MEASURING VOLUME, VOLUME FLOW, MASS FLOW OR LIQUID LEVEL; METERING BY VOLUME
    • G01F3/00—Measuring the volume flow of fluids or fluent solid material wherein the fluid passes through the meter in successive and more or less isolated quantities, the meter being driven by the flow
    • G01F3/02—Measuring the volume flow of fluids or fluent solid material wherein the fluid passes through the meter in successive and more or less isolated quantities, the meter being driven by the flow with measuring chambers which expand or contract during measurement
    • G01F3/04—Measuring the volume flow of fluids or fluent solid material wherein the fluid passes through the meter in successive and more or less isolated quantities, the meter being driven by the flow with measuring chambers which expand or contract during measurement having rigid movable walls
    • G01F3/14—Measuring the volume flow of fluids or fluent solid material wherein the fluid passes through the meter in successive and more or less isolated quantities, the meter being driven by the flow with measuring chambers which expand or contract during measurement having rigid movable walls comprising reciprocating pistons, e.g. reciprocating in a rotating body
    • G01F3/16—Measuring the volume flow of fluids or fluent solid material wherein the fluid passes through the meter in successive and more or less isolated quantities, the meter being driven by the flow with measuring chambers which expand or contract during measurement having rigid movable walls comprising reciprocating pistons, e.g. reciprocating in a rotating body in stationary cylinders

Definitions

  • This invention relates generally to flow measuring apparatus for use with a fluid flow with a flow rate, including apparatus useable as meter provers and/or positive displacement flow meters.
  • Meter provers are positive displacement devices that launch pistons in barrels, timing their travel time to deduce the flow rate. Piston travel is typically monitored in only one direction to calibrate or check accuracy of a flow meter. Provers tend to have elaborate hardware to minimize the flow rate measurement errors and are typically intended to calibrate meters used in flow lines greater than four inches in diameter. For smaller lines, the piston meter prover concept has been used to make positive displacement flow meters by providing mechanisms that allow the piston to reciprocate continuously. Reciprocation is facilitated by mechanical linkages that divert valve mechanisms or by electrically operated three or four way diverting valves to achieve piston reciprocation. Often in high pressure hydraulic systems it is desirable to measure flow rates below five gallons per day. For various reasons, a continuous flow measurement may not be required, but a reliable, accurate means tolerant to debris is desirable.
  • a flow measuring apparatus comprises a barrel having an interior area and a piston movable in the barrel between first and second positions.
  • the piston divides the interior area into first and second portions.
  • a biasing member is coupled to the piston and urges the piston toward the first position.
  • a first fluid passageway has an inlet, an outlet and an intermediate portion therebetween.
  • a second fluid passageway is in fluid communication with the first fluid passageway and with the first portion of the barrel. The second fluid passageway provides fluid from the intermediate portion of the first fluid passageway to the first portion of the barrel to move the piston toward the second position.
  • a valve assembly is coupled to the first fluid passageway downstream of the intermediate portion.
  • the valve assembly is movable between open and closed positions. In the open position the valve assembly allows fluid to pass through the first fluid passageway to the outlet. In the closed position the valve assembly causes fluid to flow into the second flow passageway and into the first portion of the chamber to move the piston from the first position to the second position.
  • the valve assembly configured to move toward the open position to release pressure from the barrel in an overpressure condition.
  • a latch mechanism is coupled to the valve assembly and is movable between an activated position and a released position.
  • the latching mechanism in the activated position moves the valve assembly to the closed position, and the latching mechanism in the released position allows the valve assembly to move to the open position.
  • the latching mechanism is configured to move to the released position at least when the piston reaches the second position.
  • An actuator is coupled to the latching mechanism and configured to activate the latch mechanism to move the valve assembly to the closed position to cause the fluid to move the piston to the second position.
  • a measuring device monitors the movement of the piston between the first and second positions through a stroke and the time to complete the stroke.
  • a biased piston is movable between first and second positions. The piston is biased toward the first position.
  • a second fluid passageway provides fluid from the intermediate portion of the first fluid passageway to a portion of the piston to move the piston toward the second position.
  • a valve is coupled to the first fluid passageway downstream of the intermediate portion.
  • the valve has a valve member movable between open and closed positions. In the open position the valve member allows the fluid flow to pass through the first fluid passageway to the fluid outlet.
  • valve member In the closed position the valve member directs the fluid flow into the second flow passageway and to the portion of the piston to move the piston from the first position to the second position.
  • the valve has a biasing member that urges the valve member with an urging force toward the closed position. The biasing member allows the valve member to move away from the closed position when fluid pressure on the valve member exerts a force that exceeds the urging force.
  • An activation mechanism is coupled to the valve and is movable between a released position wherein the valve is in the open position and an activated position that causes the valve to move to the closed position.
  • the activation mechanism moves to the released position at least when the piston reaches the second position.
  • a measuring device is configured to monitor the movement of the piston between the first and second positions through a stroke and the time to complete the stroke.
  • FIG. 1 Another aspect provides a flow measuring apparatus comprising: a cylinder having an interior area, and a piston movable in the interior area between first and second positions.
  • the piston divides the interior area into first and second portions.
  • a biasing member urges the piston toward the first position.
  • a first fluid passageway allows fluid to bypass the piston, and a second fluid passageway is in fluid communication with an intermediate portion of the first fluid passageway and with the first portion of the cylinder.
  • the second fluid passageway is configured to provide fluid from the first fluid passageway to the first portion of the cylinder to move the piston toward the second position.
  • a flow diverter is coupled to the first fluid passageway downstream of the intermediate portion.
  • the flow diverter is movable between a first flow position that allows fluid to pass through the first fluid passageway to the outlet and a second flow position that causes fluid to flow into the second flow passageway and into the first portion of the chamber to move the piston toward the second position.
  • a retention mechanism is coupled to the flow diverter and is moveable to move the flow diverter to the closed position. The retention mechanism is moveable to allow the flow diverter to move to the open position when the piston reaches the second position.
  • a sensor configured to monitor the movement of the piston between the first and second positions through a stroke and the time to complete the stroke.
  • Figure 1 is an isometric view of a flow measuring apparatus with a piston manually launched in accordance with an embodiment of the present invention.
  • Figure 2 is an isometric view of the flow measuring apparatus of Figure 1 with a portion shown in cross-section taken substantially along lines 2-2 of Figure 1.
  • Figure 3 is an enlarged cross-sectional view of a manually activatable actuator or launch mechanism taken substantially along lines 3-3 of Figure 2.
  • Figure 4 is an enlarged cross-sectional view of the flow measuring apparatus of Figure 2 with the piston in a first or dormant position prior to movement through a measurement stroke.
  • Figure 5 is an enlarged cross-sectional view of the flow measuring apparatus of Figure 2 with the piston in an intermediate portion of the measurement stroke.
  • Figure 6 is an enlarged cross-sectional view of the flow measuring apparatus of Figure 2 with the piston in a second end portion of the measurement stroke.
  • Figure 7 is an enlarged isometric view of the manual sealing pad/latching mechanism shown removed from the flow measuring apparatus of Figure 1 for purposes of clarity.
  • Figure 8 is an enlarged cross-sectional view of a portion of the flow measuring apparatus of Figure 2 showing the manual sealing pad/latching mechanism with a sealing pad in the open position.
  • Figure 9 is an enlarged cross-sectional view of a portion of the flow measuring apparatus of Figure 2 showing the manual sealing pad/latching mechanism with the sealing pad in the closed position.
  • Figure 10 is a cross-sectional view of a flow measuring apparatus in accordance with another embodiment with a solenoid launch system with a sealing pad shown in the open position.
  • Figure 11 is a cross-sectional view of a flow measuring apparatus of Figure 10 with the sealing pad in the closed position.
  • the present invention is directed toward flow measuring apparatus, including meter provers and positive displacement flow meters.
  • flow measuring apparatus including meter provers and positive displacement flow meters.
  • Several aspects of embodiments are directed toward flow measuring apparatus that include a piston moving in a barrel while compressing a return spring whilst the piston moves through its measurement stroke.
  • Other aspects of the invention are directed to a piston launched in a measurement direction by blocking a by-pass that, in the open mode, routes flow around the piston. This blockage can be achieved with a spring loaded sealing pad.
  • the sealing pad pressure is generally greater than the piston pressure to overcome the return spring.
  • the action of the sealing pad opening and closing can be of mechanical means such as linkages or by an actuator such as a solenoid.
  • the piston movement can be measured with the use of proximity sensors, with inductive means, or via other devices.
  • Figure 1 is an isometric view of a flow measuring apparatus 100 for measuring fluid flow rate in accordance with one embodiment of the invention.
  • Figure 2 is an isometric view of the flow measuring apparatus of Figure 1 with a portion shown in cross-section taken substantially along lines 2-2 of Figure 1.
  • Figure 3 is an enlarged cross-sectional view of a manually activatable launch mechanism or actuator 149 taken substantially along lines 3-3 of Figure 2.
  • the flow measuring apparatus of the illustrated embodiment is a flow meter 100 that includes an inlet body section 101 mated to a barrel 110 that has a bore 105 that houses a piston 104 (Figure 2) and a piston spring 120 (Figure 2) that urges the piston 104 along axis X1.
  • the piston 104 is sealed to the bore 105 of the barrel 110 by a seal 106 on a piston head 111.
  • the piston spring 120 is shown as a coil spring, although the piston spring could be another biasing member, such as a wave washer or Belleville washer, that provides an urging force against the piston.
  • the seal 106 is shown as a cup seal, although other seals could be used, such as an "O" ring or bellows, to maintain a seal between the piston head 111 and the interior surface of the barrel 110 that defines the bore 105.
  • the piston 104 is slideably disposed in the bore 105, and the piston head 111 and the seal 106 divide the bore 105 into first and second portions 105a and 105b.
  • a sleeve 108 that is concentric to the piston and can be made of a ferromagnetic material, such as a 400 series stainless steel on other suitable material.
  • the function of the sleeve 104 will be explained in detail below.
  • One end of the piston 104 is guided by the seal 106 and the other end is guided by a sleeve 122 that also centers the spring 120, thereby preventing the spring from rubbing and hence scoring the inside diameter of the barrel 110.
  • Affixed to the end of the barrel 110 opposite to inlet body section 101 is an end cap 103.
  • the end cap 103 supports tie rods 161 and a return tube 107 that run parallel to the barrel 110.
  • the inlet body 101 of the illustrated embodiment contains a valve assembly 125 that is activatable to direct a fluid flow from a first fluid pathway 127 extending from the inlet 102 to an outlet 152, and a second fluid pathway 129 through the return tube 107 and into the first portion 105a of the barrel's bore 105.
  • the valve assembly 125 of the illustrated embodiment includes a seat 126 that can sealably mate with a disk-shaped sealing pad 148 mounted on a stem 145.
  • the sealing pad 148 is generally made of an elastomeric material, but can be a made from other materials that can engage the seat 126 to form a fluid tight seal.
  • the sealing pad 148 is supported by a pad end 145b of the stem 145.
  • the inlet body 101 contains a latch mechanism 137 having a mounting structure 128 and a pair of pivotal levers 130 and 132 that work together to move the valve assembly 125 between open and closed positions.
  • the first lever 130 carries the stem 145 and the sealing pad 148 such that the first lever, the stem, and the sealing pad can move as a unit relative to the seat 126 between the open and closed positions.
  • the lower end of the first lever 130 has a hole 131 through which the shank end 145a of the stem 145 extends.
  • the stem 145 is secured to the lower end of the first lever 130 by a snap ring 133, although other securing devices could be used in other embodiments.
  • the hole 131 in the first lever 130, the snap ring 133, the spring 146, the stem 145, the seat pad 148 and the seat 126 are co-axial.
  • the first lever 130 is pivotally supported by the mounting structure 128 by a first dowel 134 on an upper end portion of the first lever.
  • the second lever 132 generally overlaps and is approximately parallel to the first lever 130.
  • the second lever 132 is pivotally supported by the mounting structure 128 by a dowel 136 in approximately the center of the second lever 132.
  • the first and second levers 130 and 132 are configured to releasably retain the valve assembly 125 in the closed position when the flow meter 100 is activated and to allow the latch mechanism 137 to be released and the valve assembly moved to the open position.
  • the first lever 130 has a dog 140 affixed near its center and positioned to make intermittent contact with a dog 138 affixed near the center of the second lever 132.
  • a spring 144 or other biasing device guided and supported by the mounting structure 128 engages the first lever 130 so that the dog 140 is urged toward the second lever 132.
  • the dog 140 on the first lever 130 engages a corner of the dog 138 on the second lever 132.
  • the second lever 132 is connected to another spring 142 or other biasing member supported by the mounting structure 128.
  • the spring 142 presses against the second lever 142 and urges it toward the first lever 130 so that the spring 142 urges the second lever's dog 138 against the first lever's dog 140 when the valve assembly 125 is in this closed position.
  • the dogs 138 and 140 contact each other and maintain an angular position of the first lever 130, referred to as the "latched" position, so that the valve assembly 125 is in the closed position with the sealing pad 148 sealably engaging the seat 126.
  • the sealing pad 148 blocks the fluid flow from passing through the seat 126, thereby preventing the flow from passing through the first fluid pathway 127 to the outlet 152. Instead, the fluid flow is diverted into the second fluid pathway 129, through the return tube 107 and into the barrel's first portion 105a, so as to cause the piston 104 to move axially toward the latch mechanism 137.
  • the latch mechanism 137 and the valve assembly 125 are activated to move from the unlatched and open positions to the latched and closed positions by an actuator 149 coupled to the mounting structure 128.
  • the actuator 149 is a manual device that an operator can activate to close the valve assembly 125 and divert the fluid flow into the second fluid pathway 129 so as to measure aspects of the fluid flow.
  • the manual activator 149 of the illustrated embodiment has a rotatable cam 150 adjacent to the lower end of the latch mechanism's first lever 130. The cam 150 can be rotated to engage and pivot the first lever 130, thereby moving the valve assembly 125 to the closed position with the sealing pad 148 in sealed engagement with the seat 126.
  • the cam 150 of the actuator 149 is supported on the end of a shaft 164, sealed to the inlet body 101 by a rotary cup seal 172 or any seal designed for sealing a rotating shaft.
  • the shaft 164 is supported in two places by bushings 170 and 166 concentric to the shaft 164 and affixed to inlet body 101.
  • a liner 162 is also concentric to the shaft 164, and the liner has a protrusion on its end that mates with the inlet body 101.
  • a spring 168 is coupled to the shaft 164 and it urges the rotation of the shaft 164 and the liner 162. Rotation of the liner 162 and the shaft 164 is limited by a protrusion on the end of the liner 162 moving in a pocket 174 in the inlet body 101.
  • a handle 160 is affixed and concentric to the liner 162.
  • the handle 160 is configured so an operator can grasp and rotate the handle to activate the actuator 149.
  • This rotation of the handle 160 also rotates the liner 162 and the shaft 164, thereby causing the cam 150 to rotate relative to the latch mechanism 137.
  • the rotating cam 150 presses against the first lever 130 to move the latch mechanism 137 to the latched position, thereby moving the latch assembly 125 to the closed position.
  • the sealing pad 148 which is against the seat 126, blocks off the by-pass and causes the fluid to flow into the first portion 105a of the bore 105.
  • the fluid pressure in the bore's first portion 105a builds and presses against the piston 104, thereby moving the piston axially and compressing the spring 120. Accordingly, the piston 104 begins a measurement cycle, wherein the piston moves along a measurement stroke to an end position and then returns to its starting position.
  • the latch mechanism 137 When the flow meter 100 is in the dormant state, the latch mechanism 137 is in the unlatched position and the valve assembly is in the open position, as shown in Figure 4.
  • the fluid enters the inlet 102 and flows through the seat 126 toward the sealing pad 148.
  • the sealing pad 148 does not contact the seat 126 so the fluid flows past the sealing pad, through the first fluid pathway 127, into a cavity 158 downstream of the valve assembly 125, and then to the outlet fitting 152.
  • the fluid pressure loss in the flow meter 100 due to restrictions from inlet 102 to outlet 152 is generally negligible.
  • Figure 5 shows the piston 104 in the middle of the measurement stroke. While the piston 104 is moving toward the latch mechanism 137, the position of the ferromagnetic sleeve 108 on the piston 104 also moves, and its position can be measured by inductive means, such as a Linear Variable Differential Transformer "LVDT" or a by a Hall effect sensor. In other embodiments, the piston's movement along the measurement stroke can be measured over time by other measuring techniques. The sensors are non-evasive and produce no drag opposing the movement of piston 104.
  • LVDT Linear Variable Differential Transformer
  • the end of the piston 104 opposite the piston's head 111 has a distal protrusion 124 with a smaller diameter than the head 111 or body of the piston.
  • Figure 6 shows the piston 104 at the end of the measurement stroke. In this position, the distal protrusion 124 passes though a hole 161 in the inlet body 101 and a hole 163 in first lever 130. Each hole 161 and 163 is axially aligned with the piston 104 and the protrusion 124.
  • the end of the protrusion 124 is configured to contact the second lever 132 as the piston 104 moves to the end of the measurement stroke. This contact with the latch mechanism 137, which is in the latched position, rotates the second lever 132 away from the first lever 130, which causes the dogs 138 and 140 to lose contact with each other.
  • the first lever 130 is rotated by the spring 144 reacting with the mounting structure 128, so that valve assembly 125 is moved to the open position with the sealing pad 148 moved away from the seat 126. Once the sealing pad 148 is not blocking the flow from passing through the seat 126 and along the first flow passageway 127, the piston 104 is urged in the opposite direction by the piston spring 120.
  • the sealing pad 148 of the valve assembly 125 will experience a rise in fluid pressure that is greater than the pressure exerted by compression of piston spring 120 at the completion of a measurement stroke. As best seen in Figure 6, the sealing pad 148 is downstream of the seat 126. When the valve assembly 125 is in the closed position, the spring 146 on the stem 145 urges the sealing pad 148 against the seat 126.
  • valve assembly 125 is configured to provide a "fail open” or “fail as is” condition. After the over pressure condition is alleviated, the valve assembly will return to the closed position.
  • FIGS 10 and 11 are cross-sectional views of a portion of a flow measuring apparatus 200 in accordance with another embodiment.
  • the illustrated flow measuring apparatus 200 is a flow meter configured to selectively block flow through a by-pass to move a piston 218 against spring 120 under the watch of a position measuring system, substantially as described above with reference to the flow meter 100.
  • Movement of sealing pad 148 in this alternative embodiment is controlled by a solenoid assembly 219 comprised of an armature 242 that moves along axis X 2 and is affixed to a stem shank 244a.
  • the stem shank 244a of the illustrated embodiment is cylindrical in shape and widens to house the sealing pad 148 on end 244c.
  • a sealing pad spring 206 is sandwiched between the shank end 244c and the sealing pad 148.
  • the sealing pad spring 206 can be any one of a plurality of compression spring designs such as a coil spring, wave washer, or even a rubber washer.
  • the illustrated armature 242 is made from a ferromagnetic material, while stem shank 244a need not be ferromagnetic.
  • a bonnet 248 contains oil inside of it's hollow cylinder section and has a flange 248b attached to one end that acts as the end of a bobbin to contain conductive windings 256.
  • a target 246 is made of a ferromagnetic material and is anchored to the bonnet 248.
  • the bonnet 248 of the illustrated embodiment is affixed to the body 202 by a clamp nut 264, which also protects the windings 256.
  • the target 246 is a hollow cylinder concentric to the bonnet 248, the armature 242, the stem shank 244a, the sealing pad 148, and the seat 126.
  • An outside diameter of a diaphragm 252 is affixed and sealed to the bonnet 248, and the inside diameter of the diaphragm 252 affixed and sealed to the valve stem 244c.
  • a return spring 250 is affixed on one end to the stem 244c and on the other end to the bonnet 248.
  • the diaphragm 252 provides a barrier between the ferromagnetic armature 242 bathed in oil and process fluids, thereby preventing debris from process fluids lodging between the small clearances between the armature 242 and the inside diameter of the bonnet 248, which would retard the motion of the armature 242.
  • a return spring 250 urges the sealing pad 148, the stem 244, and the sealing pad spring 206 away from the seat 126 along axis X2.
  • the piston 218 supports the ferromagnetic sleeve 108. Movement of the sleeve 108 can be detected using the LVDT principle using the three coils 112, 114, and 116 shown in Figures 10 and 11. Measuring the travel of piston 218 over time can also be achieve with other non-evasive proximity sensors, such as Hall effect sensors or a variety of evasive position sensors.
  • the piston 218 is hollow and travels over a stationary tube 214 that returns fluid from the cavity 262 that contains the piston spring 120.
  • the piston 218 has a first cup seal 106 that sealably engages the inside diameter of barrel 210.
  • the inside of piston 218 has a second cup seal 236 that sealably engages the return tube 214.
  • ferrules and washers made from ferromagnetic material to enhance the efficiency of the solenoid are not show.
  • direct current or alternating current is applied to the windings 256, the armature 242 is electromagnetically attracted to the target 246. This attractive force moves the stem shank 244, the sealing pad spring 206, and the sealing pad 148 against the seat 126 until the target 246 contacts the armature 242.
  • the force exerted by the sealing pad 148 on the seat 126 is governed by the spring tension in the sealing pad spring 206. Whilst the windings 256 are energized and the sealing pad 148 contacts the seat 126, fluid entering the inlet 204 is diverted into the chamber 260 on the cup seal side of the piston 218. Diversion of fluid to the chamber 260 causes the piston 218 to move the compressing spring 120, as shown in Figure 11. Piston-position sensors measure the rate of travel of the piston 218 over the stroke and send signals to a microprocessor to compute the flow rate.
  • the windings 256 are de-energized at the end of the measurement stroke before the piston 218 contacts the end cap 212. Once the coil windings 256 are de-energized, the armature 242 and the sealing pad 148 move away from the seat 126, which opens the by-pass and allows the piston spring 120 to urge the piston 218 back to the dormant position shown in Figure 10.
  • the piston 218 can collide with the end cap 212 without significantly damaging the flow meter 200. If these two components collide, the pressure builds under the sealing pad 148 in the inside diameter of the seat 126 until the pressure overcomes the force that the sealing pad spring 206 exerts on the seat 126.
  • flow measuring devices may include other components in lieu of the solenoid for automating the operation.
  • the condition of the piston seals, the sealing pad, and/or other components can be checked periodically without removing the flow meter from the flow line.
  • the flow meter can be checked by activating the sealing pad 148 against the seat 126 to send the piston 104 or 218 into any section of its measurement stroke.
  • a valve external to the flow meter can be used to block the flow.
  • the external valve can be connected to either the outlet or inlet of flow meter 100 or 200. If the external valve blocks the flow with no leakage through the external valve, the piston in the flow meter 100 or 200 should be suspended at some position in the measurement stroke with negligible movement.
  • the piston spring 120 will urge the piston in the opposite direction that it started on its measurement stroke.
  • the position sensors for the flow meter 100 or 200 can detect this reverse movement and report the leak of the piston seal and/or sealing pad. This feature is referred to as "self diagnostics" with all checks performed without removing the meter from the flow line.

Landscapes

  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Measuring Volume Flow (AREA)
  • Indication Of The Valve Opening Or Closing Status (AREA)

Abstract

L'invention concerne un appareil de mesure d'écoulement d'un mode de réalisation qui comprend un cylindre et un piston mobile dans le cylindre entre une première et une seconde position. Le piston divise la zone intérieure du cylindre en une première et une seconde partie. Un élément de sollicitation presse le piston vers la première position. Un premier passage de fluide permet au fluide de contourner le piston et un second passage de fluide est en communication fluide avec le premier passage de fluide et avec la première partie du cylindre. Le second passage de fluide adresse du fluide à la première partie du cylindre pour déplacer le piston vers la seconde position. Un déviateur d'écoulement est déplaçable entre une première position d'écoulement qui permet à du fluide de passer à travers le premier passage de fluide vers l'orifice de sortie et une seconde position d'écoulement qui amène du fluide à s'écouler dans le second passage d'écoulement et dans la première partie de la chambre. Un mécanisme de rétention est déplaçable pour déplacer le déviateur d'écoulement vers la position fermée et pour permettre au déviateur d'écoulement de se déplacer vers la position ouverte lorsque le piston atteint la seconde position.
EP07761599.5A 2006-04-28 2007-04-30 Appareil de mesure d'écoulement Withdrawn EP2021744A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US79570406P 2006-04-28 2006-04-28
PCT/US2007/067815 WO2007127986A2 (fr) 2006-04-28 2007-04-30 Appareil de mesure d'écoulement

Publications (2)

Publication Number Publication Date
EP2021744A2 true EP2021744A2 (fr) 2009-02-11
EP2021744A4 EP2021744A4 (fr) 2015-09-02

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07761599.5A Withdrawn EP2021744A4 (fr) 2006-04-28 2007-04-30 Appareil de mesure d'écoulement

Country Status (4)

Country Link
US (1) US7395708B2 (fr)
EP (1) EP2021744A4 (fr)
NO (1) NO20084956L (fr)
WO (1) WO2007127986A2 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7475586B2 (en) * 2006-04-07 2009-01-13 Total Meter Services Inc. Flow meter calibration apparatus and method
US9035781B2 (en) * 2007-12-29 2015-05-19 Waterstrike Incorporated Apparatus and method for automatically detecting and alerting of gas-out conditions for a gas appliance during operation
WO2012048039A1 (fr) 2010-10-05 2012-04-12 Kirchner Mark W Régulateur de débit pour forts débits et fortes chutes de pression
US8875586B2 (en) * 2011-06-22 2014-11-04 Mesa Laboratories, Inc. Gas flow meter with horizontal piston movement
US20130008262A1 (en) * 2011-06-28 2013-01-10 Edward Albert Morrell Volumetric Gas Flow Meter With Automatic Compressibility Factor Correction
US9506785B2 (en) 2013-03-15 2016-11-29 Rain Bird Corporation Remote flow rate measuring
WO2018013857A1 (fr) 2016-07-13 2018-01-18 Rain Bird Corporation Capteur d'écoulement
US10473494B2 (en) 2017-10-24 2019-11-12 Rain Bird Corporation Flow sensor
US11662242B2 (en) 2018-12-31 2023-05-30 Rain Bird Corporation Flow sensor gauge
US11874149B2 (en) 2020-04-27 2024-01-16 Rain Bird Corporation Irrigation flow sensor systems and methods of detecting irrigation flow
CN111693100B (zh) * 2020-07-27 2022-07-08 宁波华成阀门有限公司 一种大范围流量计及大范围流量测量方法
CN114887372A (zh) * 2022-05-16 2022-08-12 曹开军 带漏水保护功能的前置过滤器及控制方法
US12443208B2 (en) 2023-02-08 2025-10-14 Rain Bird Corporation Control zone devices, systems and methods

Family Cites Families (98)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1586834A (en) * 1925-02-27 1926-06-01 Augusta N Ormsby Meter
US1777261A (en) * 1928-05-17 1930-09-30 Grainger James Edward Valve
US3677288A (en) * 1970-10-08 1972-07-18 Thomas B Martin Flow control valve
US4096747A (en) * 1975-10-14 1978-06-27 Gilson Paul R Digital output, positive displacement flow meter
DE2615009C2 (de) * 1976-04-07 1983-08-11 Fa. Ernst Flitsch, 7012 Fellbach Antrieb für einen Durchflußregelhahn
US4055084A (en) * 1976-07-08 1977-10-25 Hans Wilde Liquid flow meter construction
JPS5471432A (en) * 1977-11-17 1979-06-08 Sotokazu Rikuta Flow rate constant value automatic control valve
US4176686A (en) * 1977-11-19 1979-12-04 Concordia Fluidtechnik Gmbh Flow control valve for liquids
US4361147A (en) * 1979-01-22 1982-11-30 Master Medical Corporation Flow control device for administration of intravenous fluids
US4429708A (en) * 1979-03-22 1984-02-07 Trw Inc. Fluid flow control
US4234013A (en) * 1979-06-01 1980-11-18 Sotokazu Rikuta Control valve for keeping the rate of flow at a fixed value
US4388835A (en) * 1979-08-20 1983-06-21 Universal Flow Monitors Fluid flow meter
US4372147A (en) * 1981-03-17 1983-02-08 Waugh Controls Corporation Flow meter prover apparatus and method
USRE32157E (en) * 1981-03-17 1986-05-27 Waugh Controls Corporation Flow meter prover apparatus and method
US4481805A (en) * 1981-06-03 1984-11-13 F. H. Maloney Company Meter prover apparatus and method
US4422470A (en) * 1982-07-01 1983-12-27 The Cessna Aircraft Company Flow limiting valve
US4449548A (en) * 1982-09-23 1984-05-22 United Technologies Corporation Flow control device
DE3246738C2 (de) * 1982-09-28 1987-02-05 Dr. H. Tiefenbach Gmbh & Co, 4300 Essen Mit Eigenmedium gesteuertes Hydraulikventil mit einstellbarem Durchlaßquerschnitt
GB8306852D0 (en) * 1983-03-12 1983-04-20 Lucas Ind Plc Hydraulic flow control valve
US4513777A (en) * 1983-08-22 1985-04-30 General Motors Corporation Pressure compensated flow control valve assembly for fluids containing finely divided solids
US4549426A (en) * 1983-10-28 1985-10-29 Smith Meter, Inc. Compact flow prover
US4549572A (en) * 1984-09-24 1985-10-29 General Motors Corporation Pressure compensated fluid flow regulator
US4634095A (en) * 1985-07-26 1987-01-06 Taylor Julian S Multiple stage choke valve
US4679592A (en) * 1985-10-07 1987-07-14 Teledyne Industries, Inc. Valve seat design to reduce cavitation
IN167170B (fr) * 1987-05-14 1990-09-15 Hitachi Construction Machinery
US4829808A (en) * 1987-05-15 1989-05-16 West Theodore V Flow meter prover apparatus and method
US4893649A (en) * 1988-09-30 1990-01-16 Skoglund Paul K Constant flow rate controller valve
US5052211A (en) * 1988-10-19 1991-10-01 Calibron Systems, Inc. Apparatus for determining the characteristic of a flowmeter
DE3908377A1 (de) * 1989-03-15 1990-09-27 Fluidtech Gmbh 2-wege-stromventil
US5190075A (en) * 1989-03-28 1993-03-02 Tentler Michael L Viscosity-insensitive mechanical fluid flow regulator
US4921547A (en) * 1989-07-26 1990-05-01 Vickers Incorporated Proportional priority flow regulator
US5143116A (en) * 1989-12-11 1992-09-01 Skoglund Paul K Flow regulating valve and system using the same
US5234025A (en) * 1989-12-11 1993-08-10 Skoglund Paul K Partitioned flow regulating valve
US5282490A (en) * 1989-12-18 1994-02-01 Higgs Robert E Flow metering injection controller
ATE126172T1 (de) * 1990-10-31 1995-08-15 Inventio Ag Zweikanalige gabellichtschranke in failsafe- ausführung.
EP0585386A4 (en) * 1991-05-20 1994-09-28 Computer Control Corp Flow calibrator
US5408886A (en) * 1991-05-29 1995-04-25 Gilian Instrument Corp. Positive displacement piston flow meter with internal valve
US5299775A (en) * 1991-10-15 1994-04-05 Kolze, Inc. Flow modulating control valve assembly
NO178839C (no) * 1991-11-25 1996-06-12 Ottestad Nils T Strömningsregulator for opprettholdelse av en stabil strömningsmengde av et fluidum
US5255711A (en) * 1992-08-28 1993-10-26 Hughes Aircraft Company Spring-loaded pressure regulating valve including rolling diaphragm and compensation for variation of spring force with diaphragm displacement
US5249773A (en) * 1992-11-12 1993-10-05 Kohler Co. Fluid flow regulating valve
US5295506A (en) * 1992-12-14 1994-03-22 Smith Allan L Flow control apparatus
US5280805A (en) * 1993-01-19 1994-01-25 Skoglund Paul K Flow control valve having adjustable sleeve for varying flow rate
US5971012A (en) * 1993-06-01 1999-10-26 Skoglund; Paul K. Constant flow control valve having matable piston sleeve and outlet cover
US5301713A (en) * 1993-06-01 1994-04-12 Skoglund Paul K Flow control valve having adjustable piston for varying flow rate
US5487405A (en) * 1993-06-01 1996-01-30 Skoglund; Paul K. Flow control valve having flow adjustable by variable ring
FR2710961B1 (fr) * 1993-10-05 1995-11-17 Alliedsignal Europ Services Valve à seuil à poussoir rétractile.
US5383489A (en) * 1993-10-26 1995-01-24 Flow Design, Inc. Flow control valve with enhanced flow control piston
US5427139A (en) * 1994-05-06 1995-06-27 A & H Enterprises, Inc. Metering valve with adjustable floating piston and pin assembly
DE4427905A1 (de) * 1994-08-06 1996-02-08 Teves Gmbh Alfred Ventilvorrichtung, insbesondere für hydraulische Bremsanlagen mit Blockier- und/oder Antriebsschlupfregelung
US5718410A (en) * 1995-01-27 1998-02-17 Baumann; Hans D. Small flow control valve with cartridge type seating arrangement
US5562002A (en) * 1995-02-03 1996-10-08 Sensidyne Inc. Positive displacement piston flow meter with damping assembly
SI0751448T1 (en) * 1995-06-28 2001-08-31 Siemens Building Tech Ag Flow control valve
US5655568A (en) * 1995-08-08 1997-08-12 Bhargava; Raj Passive flow regulating device
US5615708A (en) * 1995-10-23 1997-04-01 Fisher Controls International, Inc. Flow control valve with non-plugging multi-stage valve trim
US5634491A (en) * 1995-10-23 1997-06-03 Benedict; Charles Flow control valve assembly
DE19539521C2 (de) 1995-10-24 1999-01-07 Mannesmann Rexroth Ag Stromregelventil
US6026850A (en) * 1996-02-27 2000-02-22 Global Agricultural Technology And Engineering, Llc Pressure regulating valve
US5931186A (en) * 1996-03-01 1999-08-03 Skoglund; Paul K. Fluid flow control valve and actuator for changing fluid flow rate
US6041807A (en) * 1997-04-09 2000-03-28 Toyoda Koki Kabushiki Kaisha Flow control device of power steering apparatus
DE19725198A1 (de) * 1997-06-14 1998-12-17 Bosch Gmbh Robert Brennstoffeinspritzventil
US5964408A (en) * 1997-07-14 1999-10-12 Musson; Cyril D. Irrigation sprinkler and valve with flushing system
US5878766A (en) * 1997-10-20 1999-03-09 Vickers, Incorporated Pressure compensated flow control valve
EP0911714A1 (fr) * 1997-10-20 1999-04-28 Electrowatt Technology Innovation AG Vanne de réglage de débit avec un régulateur de pression intégré
US6298879B1 (en) * 1997-10-21 2001-10-09 Masco Corporation Of Indiana Stem valve stopper
EP0982838B1 (fr) * 1998-02-24 2007-04-11 Mitsubishi Denki Kabushiki Kaisha Vanne de regulation de debit motorisee
US6824379B2 (en) * 1998-04-21 2004-11-30 Synventive Molding Solutions, Inc. Apparatus for utilizing an actuator for flow control valve gates
US6568656B1 (en) * 1998-07-09 2003-05-27 Sporlan Valve Company Flow control valve with lateral port balancing
US6167906B1 (en) * 1998-07-23 2001-01-02 Hydraforce, Inc. Bi-directional flow control valve
DE69904609D1 (de) * 1998-08-24 2003-01-30 Mhi Corp Kirkland Regelventil
US6209578B1 (en) * 1998-12-23 2001-04-03 Global Agricultural Technology And Engineering, Llc Constant flow valve
US6314980B1 (en) * 1999-09-21 2001-11-13 Paul R. Beswick Pressure compensator flow control
US20010032675A1 (en) * 2000-02-29 2001-10-25 Russell Keith M. Bi-directional pressure relief valve
US6443174B2 (en) * 2000-07-08 2002-09-03 Daniel T. Mudd Fluid mass flow control valve and method of operation
AT411923B (de) * 2000-08-23 2004-07-26 Weber Gisela Hydraulikventil
GB2370096A (en) * 2000-12-18 2002-06-19 Fluid Controls U K Ltd Constant flow control valve
US6616837B2 (en) * 2001-01-03 2003-09-09 Innovative Engineering Systems, Ltd. Apparatus for the optimization of the rheological characteristics of viscous fluids
JP2002286162A (ja) * 2001-03-23 2002-10-03 Megatorr Corp 広帯域可変コンダクタンスバルブ
DE10123157C1 (de) * 2001-04-27 2002-11-14 Demag Cranes & Components Gmbh Pneumatikventil
US6601609B2 (en) * 2001-06-01 2003-08-05 Shane S. Taylor Fluid flow control valve
GB0121071D0 (en) * 2001-08-31 2001-10-24 Ashe Morris Ltd Multi-port flow control valves
US6408870B1 (en) * 2001-08-31 2002-06-25 Research By Copperhead Hill, Inc. Flow control valve
US7114700B2 (en) * 2001-09-13 2006-10-03 Beswick Engineering Metering and flow control valve
GB2379968B (en) * 2001-09-19 2003-08-27 Kvaerner Oilfield Products Ltd Liquid flow regulator
US6662823B2 (en) * 2001-11-05 2003-12-16 Samyang Comprehensive Valve Co., Ltd. Auto flow regulator
US6640830B2 (en) * 2001-12-12 2003-11-04 Sun Hydraulics Corp. Pilot operated pressure valve
US7484710B2 (en) * 2002-03-19 2009-02-03 Fisher Controls International Llc Fluid flow control valve with high temperature bi-directional shutoff
US6688319B2 (en) * 2002-04-10 2004-02-10 Flow Design, Inc. Flow regulating control valve and method for regulating fluid flow
US6751939B2 (en) * 2002-06-25 2004-06-22 Honeywell International Inc. Flow divider and ecology valve
US6966329B2 (en) * 2003-01-27 2005-11-22 Hydraforce, Inc. Proportional pilot-operated flow control valve
JP4422512B2 (ja) * 2003-04-09 2010-02-24 株式会社不二工機 可変容量型圧縮機用の制御弁
US6932107B2 (en) * 2003-06-24 2005-08-23 Flow Control Industries, Inc. Flow control valves
US7225831B2 (en) * 2003-07-25 2007-06-05 Gilmore Valve Co., Ltd. Fluid flow control valve
GB0320170D0 (en) * 2003-08-28 2003-10-01 Aesseal Plc Applications for controlling flow through a seal barrier fluid support system
JP2005112280A (ja) * 2003-10-10 2005-04-28 Kayaba Ind Co Ltd パワーステアリング装置
US7219690B2 (en) * 2004-03-11 2007-05-22 Watkins Manufacturing Corporation Flow control valve
US7156368B2 (en) * 2004-04-14 2007-01-02 Cummins Inc. Solenoid actuated flow controller valve
US7252143B2 (en) 2004-05-25 2007-08-07 Computalog Usa Inc. Method and apparatus for anchoring tool in borehole conduit

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2007127986A2 *

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US7395708B2 (en) 2008-07-08
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NO20084956L (no) 2009-01-27
WO2007127986A3 (fr) 2008-03-06
US20080006095A1 (en) 2008-01-10

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